Tag: compression gas spring

 

Posted by: | on January 14, 2025

a secondary sealing guidance structure for gas springs

Patent No.:CN208778568U Date:2018-09-11

Google Patent: https://patents.google.com/patent/CN208778568U/en?oq=CN208778568U

China Patent: http://epub.cnipa.gov.cn/

Abstract

This utility model provides a secondary sealing guidance structure for gas springs, including a piston rod, first and second guiding sealing components, a piston, and a cylinder. This utility model adds a second guiding sealing component between the piston rod and the cylinder. A movable second sealing ring is assembled in a stepped groove of this second guiding sealing component. When the gas is inflated into the gas spring through the inflation port, it passes through the first and second guiding sealing components, pushing the second sealing ring out of the stepped groove to ensure a clear inflation passage. Upon completion of inflation, under the pressure of the piston, the second sealing ring retracts into the stepped groove, blocking the inflation passage to prevent gas leakage, thus forming a secondary seal. This utility model not only ensures convenient inflation but also prevents gas leakage, offering good sealing performance and helping to extend the service life of the gas spring.

Description

Field of Technology This utility model relates to the field of gas spring technology, specifically to a secondary sealing guidance structure for gas springs.

Background Technology Gas springs need to be filled with inert gas during use. In existing technology, some gas springs have a sealing guidance component connected to the front end, inflating via the piston rod end. However, this structure, which uses only one sealing guidance component, does not have good airtightness, causing internal gas to leak easily. Additionally, to prevent gas leakage, two sets of sealing guidance components are arranged in parallel at the front end of the gas spring, improving the sealing but significantly increasing the difficulty of inflation. There are also structures with inflation ports at the rear end of the gas spring, which are not easy to seal, often resulting in defective products and low work efficiency.

Utility Model Content One objective of this utility model is to propose a secondary sealing guidance structure for gas springs that is easy to inflate, has good sealing performance, and helps to extend the service life of the gas spring.

This utility model provides a secondary sealing guidance structure for gas springs, including a piston rod, first and second guiding sealing components, a piston, and a cylinder. The first and second guiding sealing components are sequentially connected from outside to inside at the front end opening of the cylinder. The piston is slidably connected within the cylinder, with the piston’s diameter equal to the cylinder’s inner diameter. One end of the piston rod is connected to the center of the piston, while the other end passes through the first and second guiding sealing components and extends out of the cylinder. There is a gap between the piston rod and both the first and second guiding sealing components, forming an inflation port. A lip seal ring is set close to the side of the first guiding sealing component near to the second guiding sealing component, which fits onto the piston rod, allowing gas to enter while preventing gas from escaping. A stepped groove is set on the end face of the second guiding sealing component away from the first guiding sealing component, with a second sealing ring assembled between the stepped groove and the piston rod. This second sealing ring can move in and out of the stepped groove.

In this utility model, a second guiding sealing component is added between the piston rod and the cylinder, with a movable second sealing ring assembled in the stepped groove of this second guiding sealing component. When inflating the gas spring through the inflation port, gas passes through the first and second guiding sealing components, pushing the second sealing ring out of the stepped groove to ensure a clear inflation passage. Upon completion of inflation, under the piston’s pressure, the second sealing ring retracts into the stepped groove, blocking the inflation passage and preventing gas leakage, thereby forming a secondary seal of the piston rod. This utility model ensures convenient inflation while preventing gas leakage, offering good sealing performance, and helping to extend the gas spring’s service life.

Further Description

  • Additionally, a first sealing ring is arranged between the second guiding sealing component and the inner surface of the cylinder.
  • Additionally, the first sealing ring is fitted in the first groove on the outer sidewall of the second guiding sealing component.
  • Additionally, the outer sidewall of the second guiding sealing component also has a second groove, and a protrusion corresponding to the second groove is arranged on the cylinder, with the protrusion engaged in the second groove.
  • Additionally, a snap protrusion is arranged at the opening of the front end of the cylinder, and a snap groove is arranged on the first guiding sealing component corresponding to the position of the snap protrusion, with the snap protrusion engaged in the snap groove.
  • Additionally, the rear end of the cylinder is connected to a rear plug.
  • Additionally, the rear plug, cylinder, and second guiding sealing component form a sealed inner cavity of the gas spring, which is filled with inert gas.

The additional aspects and advantages of this utility model will be partially given in the following description, partially be apparent from the following description, or learned through practice of the utility model.

Brief Description of Drawings

  • Figure 1 is a schematic diagram of the secondary sealing guidance structure for gas springs in normal use state, according to an embodiment of the utility model.
  • Figure 2 is a schematic diagram of the secondary sealing guidance structure for gas springs in a high-pressure inflation state, according to an embodiment of the utility model.
  • Figure 3 is a schematic diagram of the gas spring with a secondary sealing guidance structure, according to an embodiment of the utility model.

In the drawings:

  1. Piston rod
  2. First guiding sealing component
  3. Lip seal ring
  4. Snap groove
  5. Second guiding sealing component
  6. Sleeve ring
  7. First sealing ring
  8. Second sealing ring
  9. Stepped groove
  10. First groove
  11. Second groove
  12. Piston
  13. Piston seal ring
  14. Cylinder
  15. Protrusion
  16. Snap protrusion
  17. Inert gas
  18. Rear plug

Detailed Description

The embodiments of this utility model are described in detail below, wherein the examples of these embodiments are shown in the accompanying drawings, in which the same or similar reference numerals indicate the same or similar elements or elements having the same or similar functions. The embodiments described below by reference to the figures are exemplary and are intended to explain the utility model and should not be construed as limiting the utility model.

This utility model embodiment provides a secondary sealing guidance structure for gas springs, as shown in Figures 1 and 2, including: a piston rod (1), a first guiding sealing component (2), a second guiding sealing component (3), a piston (4), and a cylinder (5). The first guiding sealing component (2) and the second guiding sealing component (3) are sequentially connected from outside to inside at the front end opening of the cylinder (5). The piston (4) is slidably connected within the cylinder (5), with the piston (4) having a diameter equal to the inner diameter of the cylinder (5). One end of the piston rod (1) is connected to the center of the piston (4), while the other end passes through the first guiding sealing component (2) and the second guiding sealing component (3) and extends out of the cylinder (5). There are gaps between the piston rod (1) and both the first guiding sealing component (2) and the second guiding sealing component (3), forming an inflation port (8). The first guiding sealing component (2) has a lip seal ring (21) near the side of the second guiding sealing component (3), which fits onto the piston rod (1), allowing gas to enter while preventing gas from escaping. The second guiding sealing component (3) has a stepped groove (34) on the end face away from the first guiding sealing component (2), with a second sealing ring (33) fitted between the stepped groove (34) and the piston rod (1). The second sealing ring (33) can move in and out of the stepped groove (34).

This utility model adds a second guiding sealing component between the piston rod and the cylinder, with a movable second sealing ring assembled in the stepped groove of this second guiding sealing component. When inflating the gas spring through the inflation port, gas passes through the first and second guiding sealing components, pushing the second sealing ring out of the stepped groove to ensure a clear inflation passage. Upon completion of inflation, under the pressure of the piston, the second sealing ring is pushed back into the stepped groove, blocking the inflation passage and preventing gas leakage, thus forming a secondary seal for the piston rod. This utility model ensures convenient inflation while preventing gas leakage, offering good sealing performance, and helping to extend the gas spring’s service life.

In one aspect of this utility model embodiment, a first sealing ring (32) is arranged between the second guiding sealing component (3) and the inner surface of the cylinder (5) and is fitted in the first groove (35) on the outer sidewall of the second guiding sealing component (3). The main body of the second guiding sealing component is an annular sleeve (31), which fits onto the piston rod (1). Preferably, the outer sidewall of the second guiding sealing component (3) also has a second groove (36), and a protrusion (51) corresponding to the second groove (36) is arranged on the cylinder (5), with the protrusion (51) engaged in the second groove (36). This design ensures the airtightness between the second guiding sealing component and the cylinder while also providing a stable connection of the second guiding sealing component on the cylinder.

In one aspect of this utility model embodiment, a snap protrusion (52) is arranged at the opening of the front end of the cylinder (5), and a snap groove (22) corresponding to the position of the snap protrusion (52) is arranged on the first guiding sealing component (2), with the snap protrusion (52) engaged in the snap groove (22). The assembly of the snap protrusion and the snap groove ensures the stable connection of the first guiding sealing component at the front end opening of the cylinder.

In one aspect of this utility model embodiment, as shown in Figure 3, the rear end of the cylinder (5) is connected to a rear plug (7), forming a sealed inner cavity of the gas spring with the cylinder (5) and the second guiding sealing component (3), which is filled with inert gas (6). The rear plug, cylinder, first guiding sealing component, and second guiding sealing component together form an inner cavity holding inert gas, providing the environment for the utility model to function.

Although the embodiments of the utility model have been shown and described above, it will be understood that the above embodiments are exemplary and should not be construed as limiting the utility model. Those skilled in the art can make changes, modifications, replacements, and variations within the scope of the utility model.

Claims: a secondary sealing guidance structure for gas springs, invented by LeiYan Gas Spring, a pioneer Chinese Gas Spring Manufacture

  1. A secondary sealing guidance structure for gas springs characterized by including:
    • a piston rod, a first guiding sealing component, a second guiding sealing component, a piston, and a cylinder;
    • where the first and second guiding sealing components are sequentially connected from outside to inside at the front end opening of the cylinder, the piston is slidably connected within the cylinder, one end of the piston rod is connected to the piston, the other end passes through the first and second guiding sealing components and extends out of the cylinder, and there are gaps between the piston rod and both the first and second guiding sealing components, forming an inflation port;
    • the first guiding sealing component has a lip seal ring on the side near the second guiding sealing component, which fits onto the piston rod;
    • the second guiding sealing component has a stepped groove on the side away from the first guiding sealing component, with a second sealing ring between the stepped groove and the piston rod, the second sealing ring can move in and out of the stepped groove.
  2. The secondary sealing guidance structure for gas springs as described in claim 1, characterized by further including a first sealing ring between the second guiding sealing component and the inner surface of the cylinder.
  3. The secondary sealing guidance structure for gas springs as described in claim 2, characterized by the first sealing ring being fitted in the first groove on the outer sidewall of the second guiding sealing component.
  4. The secondary sealing guidance structure for gas springs as described in claim 3, characterized by the second guiding sealing component’s outer sidewall also having a second groove, with a corresponding protrusion on the cylinder positioned to engage in the second groove.
  5. The secondary sealing guidance structure for gas springs as described in claim 1, characterized by the front end opening of the cylinder having a snap protrusion, with a corresponding snap groove on the first guiding sealing component, with the snap protrusion engaged in the snap groove.
  6. The secondary sealing guidance structure for gas springs as described in claims 1-5, characterized by the rear end of the cylinder being connected to a rear plug.
  7. The secondary sealing guidance structure for gas springs as described in claim 6, characterized by the rear plug, cylinder, and second guiding sealing component forming a sealed inner cavity of the gas spring, which is filled with inert gas.

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Posted by: | on January 12, 2025

Double-Cylinder Temperature Compensation Gas Spring

Patent No.:CN208778566U Date:2018-09-11

Google Patent: https://patents.google.com/patent/CN208778566U/en?oq=CN208778566U

China Patent: http://epub.cnipa.gov.cn/

Abstract

The present utility model provides a double-cylinder temperature compensation gas spring, comprising: a piston rod, an outer cylinder, a guide sealing device, a piston, an inert gas, a rear plug, a spring, a floating piston, and an inner cylinder. During use, the inert gas is filled into the chamber under high pressure, and the pressure of the gas acts on the floating piston. The spring connected to the floating piston generates a corresponding amount of compression. Since the pressure of the inert gas varies with temperature, the compression of the floating piston changes accordingly. When the temperature rises and the pressure of the inert gas increases, the floating piston is further compressed. Conversely, when the temperature drops and the pressure of the inert gas decreases, the floating piston is further extended. This way, the overall volume of the inert gas is adjusted through the change in the position of the floating piston, mitigating the effect of temperature changes on the pressure of the inert gas in the chamber and ensuring the relatively stable force output of the gas spring.

Description
A Double-Cylinder Temperature Compensation Gas Spring

Technical Field
The present utility model relates to the technical field of gas springs, and more particularly to a double-cylinder temperature compensation gas spring.

Background Technology
The gas spring operates by the pressure differential formed by the gas pressure on both sides of the gas spring piston. Since the pressure difference is determined by the area difference on both sides of the piston, the elastic force output by the gas spring is completely determined by the pressure of the gas inside it. As gas pressure is easily affected by temperature, mitigating the effect of temperature changes on the elastic force output of gas springs has become an urgent technical problem to be solved in this field.

Utility Model Content
The purpose of this utility model is to propose a double-cylinder temperature compensation gas spring that can mitigate the effect of temperature changes on the internal pressure of the gas spring.

This utility model provides a double-cylinder temperature compensation gas spring, which includes: a piston rod, an outer cylinder, a guide sealing device, a piston, an inert gas, a rear plug, a spring, a floating piston, and an inner cylinder. The guide sealing device is connected to the front-end opening of the outer cylinder, and the rear plug is connected to the rear-end opening of the outer cylinder. The outer cylinder, guide sealing device, and rear plug form the overall chamber of the gas spring. Inside the chamber, a coaxial inner cylinder is placed between the rear plug and the guide sealing device. The inner cylinder divides the chamber into an inner cavity and an outer cavity, which are connected through vent holes on the sidewall of the inner cylinder. The piston is slidably connected in the inner cavity. One end of the piston rod is connected to the piston, while the other end extends out of the outer cylinder through the guide sealing device. The diameter of the piston is slightly smaller than the inner cylinder’s diameter, and the diameter of the piston rod is slightly smaller than the inner cylinder’s diameter. Both the piston and the piston rod are coaxial with the outer cylinder. The floating piston is slidably connected in the outer cavity and is annular, with its outer ring’s diameter slightly smaller than the inner diameter of the outer cylinder and its inner ring’s diameter slightly larger than the outer diameter of the inner cylinder. The spring is installed in the outer cavity between the floating piston and the guide sealing device. Both the inner cavity and the outer cavity part of the floating piston are filled with inert gas.

During use, the inert gas is filled into the chamber under high pressure, acting on both sides of the piston. Since the piston rod and piston are riveted together, the pressure areas on both sides of the piston are different, generating an outward extension force on the piston. The internal pressure of the chamber also acts on one side of the floating piston. The floating piston is compressed by the mechanical spring corresponding to this pressure. When the unit volume of the inert gas changes due to temperature variations, the pressure changes accordingly, causing the floating piston to displace due to the pressure difference. When the temperature rises, the increased pressure of the inert gas causes the floating piston to compress further towards the auxiliary spring direction. When the temperature decreases, the floating piston displaces towards the gas chamber under the action of the auxiliary spring. This compensates for the pressure inside the gas chamber due to the changes in the total volume of inert gas caused by temperature variations, thereby reducing the effect of temperature changes on the internal pressure of the inert gas inside the chamber and ensuring the relatively stable output force of the gas spring.

Further, the vent hole is arranged on the inner wall of the inner cylinder near the rear plug.
Further, a sealing ring is arranged between the guide sealing device and the outer cylinder.
Further, a sealing ring is arranged between the guide sealing device and the inner cylinder.
Further, a sealing ring is arranged between the piston and the inner cylinder.
Further, a sealing ring is arranged between the floating piston and the inner cylinder.
Further, a sealing ring is arranged between the floating piston and the outer cylinder.

Additional aspects and advantages of the present utility model will be partially given in the description below, partially apparent from the description below, or learned through the practice of the present utility model.

Brief Description of the Drawings
Figure 1 is a schematic structural diagram of a double-cylinder temperature compensation gas spring according to an embodiment of the present utility model.
The marks in the attached drawings are as follows:
Piston rod
Outer cylinder
Guide sealing device
Piston
Inert gas
Rear plug
Spring
Floating piston
Vent hole
Inner cylinder
Inner cavity
Outer cavity
Sealing ring

Detailed Description of Preferred Embodiments
The embodiments of the present utility model will be described in detail below. The exemplary embodiments are shown in the drawings, wherein identical or similar reference numerals indicate identical or similar elements or elements having the same or similar functions throughout the drawings. The embodiments described below with reference to the accompanying drawings are illustrative and are intended to explain the present utility model, but should not be construed as limiting the present utility model.

An embodiment of the present utility model provides a double-cylinder temperature compensation gas spring, as shown in Figure 1, which includes: the piston rod 1, the outer cylinder 2, the guide sealing device 3, the piston 4, the inert gas 5, the rear plug 6, the spring 7, the floating piston 8, and the inner cylinder 10. The guide sealing device 3 is connected to the front-end opening of the outer cylinder 2, and the rear plug 6 is connected to the rear-end opening of the outer cylinder 2. The outer cylinder 2, guide sealing device 3, and rear plug 6 form the chamber of the gas spring. Additionally, a coaxial inner cylinder 10 is designed between the rear plug 6 and the guide sealing device 3, dividing the chamber into an inner cavity 11 and an outer cavity 12. The inner cavity 11 and the outer cavity 12 are connected through a vent hole 9 arranged on the sidewall of the inner cylinder 10. The piston 4 is slidably connected in the inner cavity 11. One end of the piston rod 1 is connected to the piston 4, and the other end extends out of the outer cylinder 2 through the guide sealing device 3. The diameter of the piston 4 is equal to that of the inner cylinder 10, and the diameter of the piston rod 1 is smaller than that of the inner cylinder 10. Both the piston 4 and the piston rod 1 are coaxial with the outer cylinder 2. The floating piston 8 is slidably connected in the outer cavity 12. The floating piston 8 is annular, with its outer ring surface tightly attached to the inner surface of the outer cylinder 2, and its inner ring surface tightly attached to the outer surface of the inner cylinder 10. The spring 7 is connected in the outer cavity 12 between the floating piston 8 and the guide sealing device 3. The entire inner cavity 11 and the outer cavity 12 part of the floating piston are filled with the inert gas. Here, the outer cavity on the side opposite the spring with respect to the floating piston is meant.

During use, the inert gas is filled into the chamber of the gas spring under high pressure, acting on both sides of the piston. Due to the close connection between the piston rod and the piston, the pressure areas on both sides of the piston are different, creating an outward extension force on the piston. Meanwhile, the pressure inside the chamber also acts on the floating piston, and the spring connected to it generates a corresponding amount of compression. Since the pressure of the inert gas varies with temperature changes, the displacement amount of the floating piston due to the pressure also varies. When the temperature increases and the pressure of the inert gas rises, the floating piston will further displace towards the auxiliary spring. Conversely, when the temperature decreases and the pressure of the inert gas drops, the floating piston will further displace towards the gas chamber under the action of the auxiliary spring. This compensates for the change in the total volume of the inert gas within the gas chamber, thereby reducing the effect of temperature changes on the pressure of the inert gas within the chamber and ensuring the relatively stable force output of the gas spring.

In one aspect of the embodiment of this utility model, sealing rings 13 are arranged between the guide sealing device 3 and the outer cylinder 2, between the guide sealing device 3 and the inner cylinder 10, between the piston 4 and the inner cylinder 10, between the floating piston 8 and the inner cylinder 10, and between the floating piston 8 and the outer cylinder 2. The arrangement of sealing rings ensures the air-tightness between the contact surfaces of each component, improving the performance of the gas spring.

Although the embodiments of the present utility model have been shown and described above, it is understood that these embodiments are illustrative and not restrictive. Those skilled in the art can make variations, modifications, substitutions, and alterations within the scope of the present utility model.

Claims – Double-Cylinder Temperature Compensation Gas Spring, invented by LeiYan Gas Spring, a pioneer Chinese Gas Spring Manufacture

  1. A double-cylinder temperature compensation gas spring, characterized by comprising:
    A piston rod, an outer cylinder, a guide sealing device, a piston, an inert gas, a rear plug, a spring, a floating piston, and an inner cylinder;
    The guide sealing device is connected to the front-end opening of the outer cylinder, the rear plug is fixed and sealed at the rear-end opening of the outer cylinder, and the outer cylinder, guide sealing device, and rear plug form the overall chamber of the gas spring. A coaxial inner cylinder is arranged between the rear plug and the guide sealing device, dividing the chamber into an inner cavity and an outer cavity, which are connected through a vent hole arranged on the sidewall of the inner cylinder;
    The piston is slidably connected in the inner cavity, one end of the piston rod is connected to the piston, and the other end extends out of the outer cylinder through the guide sealing device. The diameter of the piston is equal to that of the inner cylinder, the diameter of the piston rod is smaller than that of the inner cylinder, and both the piston and piston rod are coaxial with the outer cylinder;
    The floating piston is slidably connected in the outer cavity. The floating piston is annular, with its outer ring surface tightly attached to the inner surface of the outer cylinder and its inner ring surface tightly attached to the outer surface of the inner cylinder, serving a bidirectional dynamic sealing role. The spring is connected in the outer cavity between the floating piston and the guide sealing device;
    The entire inner cavity and the outer cavity part of the floating piston are filled with the inert gas.
  2. The double-cylinder temperature compensation gas spring according to claim 1, characterized in that the vent hole is arranged on the inner wall of the inner cylinder near the rear plug.
  3. The double-cylinder temperature compensation gas spring according to claim 1, characterized in that a sealing ring is arranged between the guide sealing device and the outer cylinder.
  4. The double-cylinder temperature compensation gas spring according to claim 1, characterized in that a sealing ring is arranged between the guide sealing device and the inner cylinder.
  5. The double-cylinder temperature compensation gas spring according to claim 1, characterized in that a sealing ring is arranged between the piston and the inner cylinder.
  6. The double-cylinder temperature compensation gas spring according to claim 1, characterized in that a sealing ring is arranged between the floating piston and the inner cylinder.
  7. The double-cylinder temperature compensation gas spring according to claim 1, characterized in that a sealing ring is arranged between the floating piston and the outer cylinder.

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Posted by: | on January 10, 2025

A Window Damper with Buffering Assistance during Compression

Patent No.:CN208858845U Date:2018-09-11

Google Patent: https://patents.google.com/patent/CN208858845U/en?oq=CN208858845U

China Patent: http://epub.cnipa.gov.cn/

Abstract

This utility model provides a window damper with buffering and assisting force during compression, including: a hollow piston rod assembly rod, a guide sleeve, a cylinder, a movable locking rod, a return spring, a locking block, a locking block rubber sleeve, and a positioning clamp sleeve. Using this utility model, when the car window is opened, the damper extends, at which point the return spring is in a reset state. When the locking block rubber sleeve enters the narrow cavity part of the cylinder from the wide cavity part of the cylinder, it generates a certain amount of friction with the inner wall of the narrow cavity part of the cylinder, allowing the window to stop at any angle; after the window is fully opened, if the wind blows the window, the damper will enter a compressed state. At this point, the return spring is first compressed, and the elliptical ball-shaped part on the movable locking rod moves, entering the narrow cavity part of the locking block from the wide cavity part, causing the locking block to expand outward, further increasing the friction between the locking block rubber sleeve and the narrow cavity part of the cylinder. This ensures that the opened window is not easily closed by the wind, providing a buffering and assisting force.

Description – A Window Damper with Buffering Assistance during Compression

Technical Field

This utility model belongs to the technical field of dampers, particularly to a window damper with buffering and assisting force during compression.

Background Technology

When operating windows, it’s often necessary to connect a positioning component to maintain the window’s stable state. In existing technology, the components generally used are linkage mechanisms, which, when the window is propped open, can easily be blown back by the wind, failing to effectively maintain the window’s stable open state.

Summary of the Utility Model

The objective of this utility model is to propose a damper with different damping forces during stretching and compression processes, making it easy to open the window, while preventing the window from closing at will when encountering a certain amount of wind.

This utility model provides a window damper with buffering assistance during compression, which includes a hollow piston rod, a cylinder, a movable locking rod, a return spring, a locking block, a locking block rubber sleeve, and a positioning clamp sleeve.

The cylinder’s middle part is designed with a cylinder diameter expansion opening, which divides the inner cavity of the cylinder into a front narrow cavity part and a rear wide cavity part. The movable locking rod is installed inside the cylinder’s inner cavity, with the front end of the movable locking rod coaxially connected to the hollow piston rod assembly. At the connection point of the movable locking rod and the hollow piston rod assembly, there is a spring positioning boss, whose diameter is smaller than the inner diameter of the cylinder’s narrow cavity part.

The return spring is installed on the movable locking rod, behind the spring positioning boss, and the back part of the movable locking rod is designed with an elliptical ball protrusion. The locking block is fitted outside the elliptical ball protrusion, with an internal stepped transition opening inside the locking block, which divides the internal cavity of the locking block into a front wide cavity part and a rear narrow cavity part.

The locking block rubber sleeve fits outside the locking block, with its diameter smaller than the cylinder’s wide cavity part and larger than the cylinder’s narrow cavity part. The positioning clamp sleeve is fixed at a corresponding position on the back end of the movable locking rod, with its diameter larger than the inner diameter of the cylinder’s narrow cavity part.

When the damper stretches, the locking block rubber sleeve moves from the cylinder’s wide cavity part into the narrow cavity part, creating friction with the inner wall of the narrow cavity part. This friction is greater than or equal to the maximum compression force value of the return spring.

When using this utility model, during window opening, the damper is in the stretching motion, with the locking block rubber sleeve creating friction with the inner wall of the cylinder’s narrow cavity part. This friction force is greater than or equal to the maximum compression force value of the return spring. When the window stops at any angle, if wind moves the window, the damper enters a compressed state. The return spring first compresses, moving the elliptical ball protrusion on the movable locking rod from the wide cavity part of the locking block into the narrow cavity part, expanding the locking block outward. This increases the friction between the locking block rubber sleeve and the narrow cavity part of the cylinder, preventing the window from being easily closed by the wind, providing buffering and resistance.

Further Details

Furthermore, the movable locking rod on the front side of the positioning clamp sleeve is also equipped with an anti-slip buffer rubber ring.

Further, a guide sleeve is installed at the front end opening of the cylinder. The inner diameter of the guide sleeve and the outer diameter of the hollow piston rod are slide-fitted.

Additionally, a slot is provided on the outer wall of the guide sleeve, and it is connected to the front end opening of the cylinder through the slot.

Furthermore, a rear block connecting piece is installed at the rear end opening of the cylinder.

The portion of the rear block connecting piece located inside the cylinder has a circular groove that is coaxial with the movable locking rod.

Further, the cylinder diameter expansion opening and the stepped transition opening are both arc-shaped transitions.

Additional aspects and advantages of this utility model will be partially illustrated in the following description, partially become apparent from the description, or be learned through the practice of this utility model.

Description of Drawings

Figure 1 is a schematic structural diagram of a window damper with buffering assistance during compression according to an embodiment of this utility model.

Figure 2 is a schematic structural diagram of the stretched state of the window damper with buffering assistance during compression according to an embodiment of this utility model.

Figure 3 is a schematic structural diagram of the compressed state of the window damper with buffering assistance during compression according to an embodiment of this utility model.

Reference Marked in the Drawings:

1 – Hollow piston rod assembly 2 – Guide sleeve 2 – Slot 3 – Cylinder 31 – Cylinder diameter expansion opening 4 – Movable locking rod 41 – Spring positioning boss 42 – Elliptical ball protrusion 5 – Return spring 6 – Locking block 61 – Stepped transition opening 7 – Locking block rubber sleeve 8 – Anti-slip buffer rubber ring 9 – Positioning clamp sleeve 10 – Rear block connecting piece 101 – Groove

Specific Embodiments

The embodiments of this utility model are described in detail below. The examples of the embodiments are shown in the drawings, where the same or similar reference numbers indicate the same or similar elements or elements having the same or similar functions. The embodiments described below with reference to the drawings are exemplary and are intended to explain this utility model rather than to limit it.

The embodiments of this utility model provide a window damper with buffering assistance during compression, as shown in Figure 1, including a hollow piston rod assembly (1), a cylinder (3), a movable locking rod (4), a return spring (5), a locking block (6), a locking block rubber sleeve (7), and a positioning clamp sleeve (9).

When describing this utility model, the position of the hollow piston rod assembly (1) is considered the front, and the position of the positioning clamp sleeve (9) is considered the rear. The middle part of the cylinder (3) is provided with a cylinder diameter expansion opening (31), which divides the inner cavity of the cylinder (3) into a front narrow cavity part and a rear wide cavity part. The movable locking rod (4) can move telescopically inside the inner cavity of the cylinder (3). The front end of the movable locking rod (4) is coaxially connected to the hollow piston rod assembly (1). At the connection point of the movable locking rod (4) and the hollow piston rod assembly (1), a spring positioning boss (41) is designed, with a diameter smaller than the inner diameter of the cylinder’s narrow cavity part. The return spring (5) is installed on the movable locking rod (4) behind the spring positioning boss (41). The back part of the movable locking rod (4) is also designed with an elliptical ball protrusion (42).

The locking block (6) is fitted outside the elliptical ball protrusion (42), with an internal stepped transition opening (61) inside the locking block (6), dividing its internal cavity into a front wide cavity part and a rear narrow cavity part. The locking block rubber sleeve (7) is fitted outside the locking block (6), with a diameter smaller than the cylinder’s wide cavity part but slightly larger than the cylinder’s narrow cavity part. Preferably, the locking block is made of high-tenacity elastic material. The positioning clamp sleeve (9) is fixedly connected to the rear end of the movable locking rod (4), with a diameter smaller than the internal diameter of the cylinder’s narrow cavity part. The positioning clamp sleeve prevents the movable locking rod from slipping out and stays in the cylinder’s wide cavity part when the car window is closed.

When the damper stretches, the locking block rubber sleeve (7) moves from the cylinder’s wide cavity part into the narrow cavity part, creating a certain amount of friction with the inner wall of the narrow cavity part. This friction amount is determined based on different car window weights, ensuring it’s light enough for the window to stay open at any angle but also greater or equal to the maximum compression force value of the return spring (5).

Preferably, the cylinder diameter expansion opening (31) and the stepped transition opening (61) are both arc-shaped transitions to ensure smooth movement of the locking block rubber sleeve and the elliptical ball protrusion without causing jamming.

When using this utility model, as shown in Figure 2, the damper is in the stretched state when the window is opened. The locking block rubber sleeve (7) moves from the cylinder’s wide cavity part into the narrow cavity part, creating the necessary friction with the inner wall of the cylinder’s narrow cavity part. This friction amount is determined based on the car window’s size and weight but also must be greater or equal to the maximum compression force value of the return spring (5) for the window to stay in place at any position. When the window is fully opened, if wind moves the window, as shown in Figure 3, the damper enters a compressed state. At this point, the return spring (5) is compressed, and the elliptical ball protrusion (42) moves from the wide cavity part of the locking block (6) into the narrow cavity part, causing the locking block (6) to expand outward. This increases the friction between the locking block rubber sleeve (7) and the narrow cavity part of the cylinder, preventing the opened window from being closed by the wind and providing buffering assistance.

Further Implementation of the Utility Model

In one aspect of the embodiments of this utility model, an anti-slip buffer rubber ring (8) is also installed on the movable locking rod (4) at the front side of the positioning clamp sleeve (9). The anti-slip buffer rubber ring compensates for the excessive movement caused by the assembly gap of components like the locking block and mitigates the impact on the positioning clamp sleeve.

In one aspect of the embodiments of this utility model, a guide sleeve (2) is connected to the front end opening of the cylinder (3). The inner diameter of the guide sleeve (2) is slide-fitted with the diameter of the hollow piston rod assembly (1). A slot (21) is designed on the outer wall of the guide sleeve (2), and the guide sleeve (2) is pressed and positioned connected to the front end opening of the cylinder (3) through the slot (21). The setup of the guide sleeve and the slot ensures the precise coaxial connection of the hollow piston rod assembly and the front end of the cylinder, enhancing tensile strength and movement stability.

In one aspect of the embodiments of this utility model, a rear block connecting piece (10) is connected to the rear end opening of the cylinder (3). Portions of the rear block connecting piece (10) within the cylinder (3) have a circular groove (101) coaxial with the movable locking rod. The design of the rear block connecting piece serves a dual purpose: it connects the damper to the window and limits the position of the movable locking rod within the cylinder. When the window is closed under human force, the locking block and locking block rubber sleeve are fully retracted into the wide cavity part of the cylinder. The return spring naturally opens in the wide cavity part of the cylinder, and the elliptical ball protrusion retracts into the wide cavity part of the locking block.

Although the embodiments of this utility model have been shown and described above, it is understood that the above embodiments are exemplary and not to be construed as limiting this utility model. Those skilled in the field can make variations, modifications, replacements, and alterations to the above embodiments within the scope of this utility model.

Claims – A Window Damper with Buffering Assistance during Compression,  invented by LeiYan Gas Spring, a pioneer Chinese Gas Spring Manufacture

  1. A window damper with buffering assistance during compression, characterized by:
    • A hollow piston rod assembly, a cylinder, a movable locking rod, a return spring, a locking block, a locking block rubber sleeve, and a positioning clamp sleeve;
    • The middle part of the cylinder is provided with a cylinder diameter expansion opening, which divides the inner cavity of the cylinder into a front narrow cavity part and a rear wide cavity part;
    • The movable locking rod is telescopically installed inside the inner cavity of the cylinder, with the front end of the movable locking rod coaxially connected to the hollow piston rod assembly. The rear side of the connection point between the movable locking rod and the hollow piston rod assembly is provided with a spring positioning boss. The diameter of the spring positioning boss is smaller than the inner diameter of the cylinder’s narrow cavity part. The return spring is installed on the movable locking rod behind the spring positioning boss. The movable locking rod on the rear side of the return spring is also provided with an elliptical ball protrusion;
    • The locking block is sleeved on the outer side of the elliptical ball protrusion, and the internal cavity of the locking block is provided with a stepped transition opening, dividing its internal cavity into a front wide cavity part and a rear narrow cavity part. The locking block rubber sleeve is sleeved on the outer side of the locking block. The outer diameter of the locking block rubber sleeve is smaller than the inner diameter of the cylinder’s wide cavity part but larger than the inner diameter of the cylinder’s narrow cavity part;
    • The positioning clamp sleeve is fixedly connected to the rear end of the movable locking rod, and its outer diameter is larger than the inner diameter of the cylinder’s narrow cavity part;
    • When the damper stretches, the locking block rubber sleeve moves from the cylinder’s wide cavity part into the narrow cavity part, creating friction with the inner wall of the narrow cavity part. This friction force is greater than or equal to the maximum compression force of the return spring.
  2. The window damper with buffering assistance during compression according to claim 1, characterized by:
    • The positioning clamp sleeve’s front side of the movable locking rod is also fitted with an anti-slip buffer rubber ring.
  3. The window damper with buffering assistance during compression according to claim 1, characterized by:
    • A guide sleeve is fixed at the front end opening of the cylinder. The inner diameter of the guide sleeve is greater than that of the hollow piston rod assembly, which slides within the guide sleeve.
  4. The window damper with buffering assistance during compression according to claim 3, characterized by:
    • A slot is provided on the outer wall of the guide sleeve, and the guide sleeve is fastened to the front end opening of the cylinder through the slot.
  5. The window damper with buffering assistance during compression according to claim 1, characterized by:
    • A rear block connecting piece is connected to the rear end opening of the cylinder.
  6. The window damper with buffering assistance during compression according to claim 5, characterized by:
    • Portions of the rear block connecting piece within the cylinder have a circular groove that is coaxial with the movable locking rod.
  7. The window damper with buffering assistance during compression according to any of claims 1-6, characterized by:
    • Both the cylinder diameter expansion opening and the stepped transition opening are arc-shaped transitions.

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Posted by: | on January 9, 2025

Dual-Sided Anti-Rotation Linear Telescopic Electric Compressed Gas Spring

Patent No.:CN207934684U Date:2017-07-11

Google Patent: https://patents.google.com/patent/CN207934684U/en?oq=CN207934684U

China Patent: http://epub.cnipa.gov.cn/

Abstract: 

This utility model proposes a dual-sided anti-rotation linear telescopic electric compressed gas spring, which includes a cylinder with a drive device installation section. The outer end of the drive device installation section is equipped with an anti-rotation sealing rear plug. The part of the cylinder close to this installation section is equipped with drive device fasteners and a first sealing guide assembly. A screw and a piston nut are installed inside the cylinder. One end of the screw matches the first sealing guide assembly. The outer edge of the piston nut slides along the inner wall of the cylinder. An anti-rotation structure is set within the cylinder to limit the rotation of the piston nut. A piston rod fixedly connected to the piston nut is installed on the other side of the cylinder. The other side of the cylinder is equipped with a second sealing guide assembly.

This utility model uses an electric drive device as a compensating force, eliminating the need for the user to apply external force. An anti-rotation sealing rear plug is installed at one end of the cylinder, and an anti-rotation structure to limit the rotation of the piston nut is set within the cylinder. The anti-rotation structure and the anti-rotation sealing rear plug form a dual-sided anti-rotation structure, improving the structural stability of the gas spring and extending its service life.

Description – Dual-Sided Anti-Rotation Linear Telescopic Electric Compressed Gas Spring

Technical Field: This utility model relates to a dual-sided anti-rotation linear telescopic electric compressed gas spring.

Background Technology: Currently, existing electric push rods have a mechanical spring structure. When in use, the elastic force of the mechanical spring tends to decay over time due to being in a compressed state for long periods, resulting in a shorter service life. Electric push rods with a mechanical spring structure are not only large in size but also have low output force, requiring wide and deep tailgate rain grooves, affecting the tailgate design, and leading to higher direct and indirect costs. Gas springs are industrial accessories that can support, cushion, brake, adjust height, and adjust angle. When used, gas springs have significant advantages over mechanical springs: they have a relatively slow speed, minimal dynamic force changes, and are easy to control, making them quite popular. Therefore, how to provide an electric push rod with a gas spring structure that is stable, cost-effective, and has a long service life is a technical problem that needs to be addressed by professionals in this field.

In light of this, the utility model is proposed.

Content of the Utility Model: The utility model aims to address at least one of the technical problems in the related technology to some extent. To achieve this, the utility model proposes a dual-sided anti-rotation linear telescopic electric compressed gas spring. The specific technical scheme is as follows:

A dual-sided anti-rotation linear telescopic electric compressed gas spring, including a cylinder storing power gas, with one side of the cylinder provided with a drive device installation section. A drive device is installed within the drive device installation section, and the outer end of the drive device installation section is equipped with an anti-rotation sealing rear plug to secure the drive device. The part of the cylinder near the drive device installation section is sequentially provided with drive device fasteners and a first sealing guide assembly from the outside in. A screw connected to the drive device and a piston nut threaded to the screw are installed inside the cylinder. One end of the screw is placed inside the first sealing guide assembly and matches the first sealing guide assembly. The outer edge of the piston nut slides along the inner wall of the cylinder, and an anti-rotation structure to limit the rotation of the piston nut is set along the length of the inner wall of the cylinder. The other side of the cylinder is equipped with a piston rod fixedly connected to the piston nut, and the end of the other side of the cylinder is equipped with a second sealing guide assembly matching the piston rod.

According to the dual-sided anti-rotation linear telescopic electric compressed gas spring provided by the utility model, the electric drive device serves as a compensating force, eliminating the need for users to apply external force. An anti-rotation sealing rear plug is installed at the first end of the cylinder to secure the drive device and prevent shaking or shifting during operation. Additionally, an anti-rotation structure to limit the rotation of the piston nut is set within the cylinder, and this anti-rotation structure, along with the anti-rotation sealing rear plug, forms a dual-sided anti-rotation structure, further improving the structural stability of the gas spring and extending its service life.

Additionally, the dual-sided anti-rotation linear telescopic electric compressed gas spring according to the above embodiments of the utility model may have the following additional technical features:

  1. According to one example of the utility model, the anti-rotation structure comprises multiple anti-rotation grooves or protrusions axially extending along the inner wall of the cylinder, and the outer edge of the piston nut is provided with multiple anti-rotation protrusions or grooves that match the inner wall of the cylinder.
  2. According to one example of the utility model, the anti-rotation structure comprises an anti-rotation sleeve installed on the inner wall of the cylinder, and the inner wall of the anti-rotation sleeve is provided with multiple anti-rotation grooves or protrusions axially extending along the sleeve, and the outer edge of the piston nut is provided with multiple anti-rotation protrusions or grooves that match the anti-rotation sleeve.
  3. According to one example of the utility model, the middle part of the anti-rotation sealing rear plug is provided with an anti-rotation connection hole that matches an external anti-rotation connection member, a drive device outlet hole below the anti-rotation connection hole, and the outer edge of the anti-rotation sealing rear plug is provided with an anti-rotation shoulder that matches the positioning anti-rotation notch at the end of the cylinder, and the outer edge of the anti-rotation sealing rear plug is further provided with a limit groove and a waterproof sealing groove that match the inner wall of the cylinder.
  4. According to one example of the utility model, the first sealing guide assembly comprises bearings and multiple guide sleeves arranged at intervals from the inside to the outside of the cylinder, and the outer edges of the guide sleeves and bearings are connected to the inner wall of the cylinder, and seals are installed between the bearings and guide sleeves and between the two guide sleeves.
  5. According to one example of the utility model, the second sealing guide assembly comprises at least two guide sleeves arranged at intervals and seals installed between the guide sleeves.
  6. According to one example of the utility model, the drive device comprises a motor connected to the anti-rotation sealing rear plug and a reducer connected to the motor and the screw.
  7. According to one example of the utility model, the drive device fastener is a reducer anti-rotation combined fixing member installed between the reducer and the first sealing guide assembly, and the reducer anti-rotation combined fixing member is connected to the inner wall of the reducer and the cylinder.
  8. According to one example of the utility model, the screw is a multi-head screw, and the piston nut is a multi-head nut that matches the multi-head screw.
  9. According to one example of the utility model, the power gas is an inert gas.

The additional aspects and advantages of the utility model will be partially given in the following description and will become apparent from the following description or through the practice of the utility model.

Description of Drawings:

  • Figure 1 is a structural schematic diagram of the dual-sided anti-rotation linear telescopic electric compressed gas spring of this embodiment.
  • Figure 2 is an anti-rotation structure of the dual-sided anti-rotation linear telescopic electric compressed gas spring of this embodiment.
  • Figure 3 is a piston nut of the dual-sided anti-rotation linear telescopic electric compressed gas spring of this embodiment.
  • Figure 4 is another anti-rotation structure of the dual-sided anti-rotation linear telescopic electric compressed gas spring of this embodiment.
  • Figure 5 is another piston nut of the dual-sided anti-rotation linear telescopic electric compressed gas spring of this embodiment.
  • Figure 6 is a structural schematic diagram of the anti-rotation sealing rear plug (one) of the dual-sided anti-rotation linear telescopic electric compressed gas spring of this embodiment.
  • Figure 7 is a structural schematic diagram of the anti-rotation sealing rear plug (two) of the dual-sided anti-rotation linear telescopic electric compressed gas spring of this embodiment.
  • Figure 8 is a structural schematic diagram of the anti-rotation sealing rear plug (three) of the dual-sided anti-rotation linear telescopic electric compressed gas spring of this embodiment.

In the figures:

  1. Cylinder
  2. Drive Device Installation Section
  3. Screw
  4. Piston Nut
  5. Air Passage Hole
  6. Anti-Rotation Structure
  7. Hollow Piston Rod
  8. Anti-Rotation Sealing Rear Plug
  9. Anti-Rotation Connection Hole
  10. Outlet Hole
  11. Anti-Rotation Shoulder
  12. Limit Slot
  13. Waterproof Sealing Groove
  14. First Sealing Guide Assembly
  15. Bearing
  16. Guide Sleeve
  17. Seal
  18. Second Sealing Guide Assembly
  19. Drive Device
  20. Drive Device Fastener
  21. Anti-Rotation Protrusion
  22. Anti-Rotation Groove
  23. Motor
  24. Reducer

Specific Implementation Method: The following describes the embodiments of this utility model in detail. The examples of the embodiments are shown in the figures, where the same or similar reference numbers throughout indicate the same or similar elements or elements with the same or similar functions. The embodiments described below with reference to the figures are exemplary and intended to explain this utility model, and should not be understood as limiting this utility model.

The dual-sided anti-rotation linear telescopic electric compressed gas spring according to the utility model is described in detail with reference to the figures.

As shown in Figure 1, this embodiment provides a dual-sided anti-rotation linear telescopic electric compressed gas spring, including a cylinder (1) storing power gas. One side of the cylinder (1) is provided with a drive device installation section (101), and a drive device (9) is installed inside the drive device installation section (101). The outer end of the drive device installation section (101) is equipped with an anti-rotation sealing rear plug (6) to secure the drive device, preventing shaking or shifting during operation. The part of the cylinder (1) near the drive device installation section (101) is sequentially provided with a drive device fastener (10) and a first sealing guide assembly (7) from the outside in. Inside the cylinder (1), a screw (2) connected to the drive device (9) and a piston nut (3) threaded to the screw (2) are installed. One end of the screw (2) is placed inside the first sealing guide assembly (7) and matches the first sealing guide assembly (7). The outer edge of the piston nut (3) slides along the inner wall of the cylinder (1), and an anti-rotation structure (4) to limit the rotation of the piston nut (3) is set along the length of the inner wall of the cylinder (1). The other side of the cylinder (1) is equipped with a hollow piston rod (5) fixedly connected to the piston nut (3), and the end of the other side of the cylinder (1) is equipped with a second sealing guide assembly (8) matching the hollow piston rod (5).

Specifically, in this embodiment, the screw (2) is a multi-head screw, and the piston nut (3) is formed by designing a multi-head nut inside the piston. The multi-head nut and piston can be integrally injection molded, and the piston nut (3) slides along the inner wall of the cylinder (1) under the rotation of the screw (2).

As shown in Figures 6-8, the middle part of the anti-rotation sealing rear plug (6) in this embodiment is provided with an anti-rotation connection hole (601) that matches the motor. The anti-rotation connection hole (601) is riveted to the connector to secure the motor, and an outlet hole (602) for the drive device leads is provided below the anti-rotation connection hole (601). The outer edge of the anti-rotation sealing rear plug (6) is sequentially provided with an anti-rotation shoulder (603) that matches the anti-rotation notch of the cylinder (1), a limit slot (604) that matches the inner wall of the cylinder, and a waterproof sealing groove (605) from the outside in. The anti-rotation sealing rear plug (6) not only functions as a waterproof seal but also combines with the cylinder (1) to form an anti-rotation structure, longitudinally positioning the motor to prevent movement and providing an outlet hole to align the motor’s power and signal wires. Additionally, it ensures the anti-rotation performance and pull-out strength after crimping the anti-rotation rear plug and the cylinder.

The anti-rotation structure (4) in this embodiment has various forms. For example, as shown in Figures 2 and 3, the anti-rotation structure (4) comprises multiple anti-rotation protrusions (11) arranged along the length of the inner wall of the cylinder, and the outer edge of the piston nut (3) is provided with multiple anti-rotation grooves (12) that match the anti-rotation protrusions. Additionally, the piston nut (3) is provided with air passage holes (301). More specifically, in this embodiment, four anti-rotation protrusions (11) are symmetrically distributed on the anti-rotation structure (4), and the piston nut (3) is provided with four anti-rotation grooves (12) that match them.

As shown in Figures 4 and 5, another example of the anti-rotation structure (4) is an anti-rotation sleeve installed on the inner wall of the cylinder, which is tightly connected to the inner wall of the cylinder (1). The inner wall of the anti-rotation sleeve is provided with multiple anti-rotation grooves (12) extending along its length, and the outer edge of the piston nut (3) is provided with multiple anti-rotation protrusions (11) that match the anti-rotation grooves (12). This structure can effectively limit the rotation of the piston nut (3). Of course, the structure is not limited to this, and other anti-rotation structures known to those skilled in the art are also within the scope of protection of this embodiment, which will not be described one by one here.

As shown in Figure 1, the first end of the cylinder (1) has a drive device installation section (101), specifically, the drive device (9) consists of a motor (13) and a reducer (14) connected to it. The motor (13) is connected to the anti-rotation sealing rear plug (6), and the reducer (14) is fixed to the inner wall of the cylinder using the drive device fastener (10). The reducer (14) is connected to the screw (2), more specifically, one end of the screw is inserted into the internal spline of the reducer, and the other part of the screw (2) is also installed in the sealing guide assembly (7).

By rotating the motor (13), the screw (2) is driven to rotate, thereby sliding the piston nut (3) and providing compensating force. The drive device fastener (10) is a reducer anti-rotation combined fixing member installed between the reducer (14) and the first sealing guide assembly (7), and it is connected to the inner wall of the reducer (14) and the cylinder (1), functioning to fix the reducer (14) and prevent its rotation. The motor in this embodiment preferably uses a 9V-12V DC power supply, and the motor is equipped with interfaces for power input, speed, and direction decoding signal output (not shown). The electronic control part of the motor is implemented by an external controller, which can be selected according to functional needs, and will not be described in detail here.

Additionally, to further improve structural stability and sealing performance, this embodiment is equipped with a first sealing guide assembly (7) and a second sealing guide assembly (8) at the left and right ends of the cylinder (1). The first end of the screw (2) is guided and fixed by the first guide sealing assembly (7), and the hollow piston rod (5) is guided and fixed by the second sealing guide assembly (8). Specifically, as shown in Figure 1, the first sealing guide assembly (7) includes bearings (701) and two guide sleeves (702) arranged at intervals from the inside to the outside of the cylinder. The bearings (701) can be directly installed in the cylinder (1) or connected to the cylinder through a bearing fixing sleeve to improve installation stability. The outer edges of the guide sleeves (702) and bearings (701) are connected to the inner wall of the cylinder (1), and seals (703) are installed between the bearings (701) and guide sleeves (702) and between the two guide sleeves. The second sealing guide assembly (8) includes two guide sleeves arranged at intervals and seals installed between the guide sleeves. The guide sleeves of the first sealing guide assembly (7) and the second sealing guide assembly (8) serve to provide a certain limit during the rotation of the screw and the telescoping of the piston rod, preventing the screw or piston from deviating, and the seals can be of sealing ring structure.

It should be noted that in the above description, “first end” refers to the upward direction in Figure 1, and “second end” refers to the downward direction in Figure 1. Other positional terms used in this embodiment to describe Figure 1 follow the same logic.

Advantages: In this embodiment, the preferred power gas is an inert gas. Compared to the electric push rods currently used in the market, inert gas has the advantages of low noise, long lifespan, small size, precise force, and low production cost.

Summary of Beneficial Effects:

  1. The electric drive device serves as a compensating force, eliminating the need for users to apply external force, making it labor-saving and convenient.
  2. An anti-rotation sealing rear plug is installed at one end of the cylinder to secure the drive device, preventing shaking or shifting during operation. Additionally, an anti-rotation structure to limit the rotation of the piston nut is set within the cylinder. The anti-rotation structure and the anti-rotation sealing rear plug form a dual-sided anti-rotation structure, further improving the structural stability of the gas spring and extending its service life.
  3. One end of the screw is guided and fixed by the first guide sealing assembly, and the hollow piston rod is guided and fixed by the second sealing guide assembly, enhancing structural stability and sealing performance.
  4. Using inert gas as the power gas offers the advantages of low noise, long lifespan, small size, precise force, and low production cost.

Terminology Clarification: In the description of this utility model, it should be understood that terms like “center,” “longitudinal,” “transverse,” “length,” “width,” “thickness,” “up,” “down,” “front,” “back,” “left,” “right,” “vertical,” “horizontal,” “top,” “bottom,” “inside,” “outside,” “clockwise,” “counterclockwise,” “axial,” “radial,” “circumferential,” and other positional or directional terms are based on the orientation or positional relationships shown in the figures. They are for the purpose of describing this utility model and simplifying the description, not to indicate or imply that the referred devices or elements must have specific orientations, constructions, or operations. Therefore, they should not be understood as limiting this utility model.

Broad Interpretation of Terms: In this utility model, unless otherwise specified and defined, terms like “installation,” “connection,” “fixing,” etc., should be understood broadly. For example, they can refer to fixed connections, detachable connections, or integral connections; they can be mechanical connections or electrical connections; they can be direct connections or indirect connections through intermediaries, or they can be connections or interactions between the interiors of two elements. Those skilled in the art can understand the specific meanings of these terms in this utility model based on specific circumstances.

In this utility model, unless otherwise specified and defined, the first feature being “above” or “below” the second feature can mean the first and second features are in direct contact, or they can be in indirect contact through intermediaries. Furthermore, the first feature being “above,” “above,” or “on top” of the second feature can mean the first feature is directly above or diagonally above the second feature, or it simply indicates the first feature is at a higher horizontal level than the second feature. The first feature being “below,” “below,” or “underneath” the second feature can mean the first feature is directly below or diagonally below the second feature, or it simply indicates the first feature is at a lower horizontal level than the second feature.

Comprehensive Description: In the description of this utility model, the terms “one embodiment,” “some embodiments,” “example,” “specific example,” or “some examples,” etc., mean specific features, structures, materials, or characteristics described in connection with the embodiment or example are included in at least one embodiment or example of this utility model. Furthermore, the described specific features, structures, materials, or characteristics can be combined in suitable ways in any one or more embodiments or examples. Additionally, it is clear to those skilled in the art that different embodiments or examples described in this utility model and their features can be combined and combined without conflicting with each other.

Disclaimer: While the utility model has been shown and described through the embodiments, it is understood that the embodiments are exemplary and not restrictive of this utility model. Those skilled in the art can make changes, modifications, substitutions, and variations to the embodiments within the scope of the utility model.

Claims: Dual-Sided Anti-Rotation Linear Telescopic Electric Compressed Gas Spring,  invented by LeiYan Gas Spring, a pioneer Chinese Gas Spring Manufacture

  1. A dual-sided anti-rotation linear telescopic electric compressed gas spring, characterized by: Including a cylinder storing power gas, with one side of the cylinder provided with a drive device installation section. A drive device is installed within the drive device installation section, and the outer end of the drive device installation section is equipped with an anti-rotation sealing rear plug to secure the drive device. The part of the cylinder near the drive device installation section is sequentially provided with drive device fasteners and a first sealing guide assembly from the outside in. Inside the cylinder, a screw connected to the drive device and a piston nut threaded to the screw are installed. One end of the screw is placed inside the first sealing guide assembly and matches the first sealing guide assembly. The outer edge of the piston nut slides along the inner wall of the cylinder, and an anti-rotation structure to limit the rotation of the piston nut is set within the inner wall of the cylinder. The other side of the cylinder is equipped with a piston rod fixedly connected to the piston nut, and the end of the other side of the cylinder is equipped with a second sealing guide assembly matching the piston rod.
  2. The dual-sided anti-rotation linear telescopic electric compressed gas spring according to claim 1, characterized by: The anti-rotation structure comprises multiple anti-rotation grooves or protrusions axially extending along the inner wall of the cylinder, and the outer edge of the piston nut is provided with multiple anti-rotation protrusions or grooves that match the inner wall of the cylinder.
  3. The dual-sided anti-rotation linear telescopic electric compressed gas spring according to claim 1, characterized by: The anti-rotation structure comprises an anti-rotation sleeve installed on the inner wall of the cylinder. The inner wall of the anti-rotation sleeve is provided with multiple anti-rotation grooves or protrusions axially extending along the sleeve, and the outer edge of the piston nut is provided with multiple anti-rotation protrusions or grooves that match the anti-rotation sleeve.
  4. The dual-sided anti-rotation linear telescopic electric compressed gas spring according to claim 1, characterized by: The middle part of the anti-rotation sealing rear plug is provided with an anti-rotation connection hole that matches an external anti-rotation connection member. A drive device outlet hole is provided below the anti-rotation connection hole. The outer edge of the anti-rotation sealing rear plug is provided with an anti-rotation shoulder that matches the positioning anti-rotation notch at the end of the cylinder, and the outer edge of the anti-rotation sealing rear plug is further provided with a limit groove and a waterproof sealing groove that match the inner wall of the cylinder.
  5. The dual-sided anti-rotation linear telescopic electric compressed gas spring according to claim 1, characterized by: The first sealing guide assembly comprises bearings and multiple guide sleeves arranged at intervals from the inside to the outside of the cylinder, and the outer edges of the guide sleeves and bearings are connected to the inner wall of the cylinder. Seals are installed between the bearings and guide sleeves and between the two guide sleeves.
  6. The dual-sided anti-rotation linear telescopic electric compressed gas spring according to claim 1, characterized by: The second sealing guide assembly comprises at least two guide sleeves arranged at intervals and seals installed between the guide sleeves.
  7. The dual-sided anti-rotation linear telescopic electric compressed gas spring according to claim 1, characterized by: The drive device comprises a motor connected to the anti-rotation sealing rear plug and a reducer connected to the motor and the screw.
  8. The dual-sided anti-rotation linear telescopic electric compressed gas spring according to claim 7, characterized by: The drive device fastener is a reducer anti-rotation combined fixing member installed between the reducer and the first sealing guide assembly, and the reducer anti-rotation combined fixing member is connected to the inner wall of the reducer and the cylinder.
  9. The dual-sided anti-rotation linear telescopic electric compressed gas spring according to claim 1, characterized by: The screw is a multi-head screw, and the piston nut is a multi-head nut that matches the multi-head screw.
  10. The dual-sided anti-rotation linear telescopic electric compressed gas spring according to claim 1, characterized by: The power gas is an inert gas.

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Posted by: | on January 8, 2025

Compressed Gas Spring with Floating Vibration Damping

Patent No.:CN205896005U Date:2016-08-23

Google Patent: https://patents.google.com/patent/CN205896005U/en?oq=CN205896005U

China Patent: http://epub.cnipa.gov.cn/

Abstract:

The utility model relates to a compressed gas spring with floating vibration damping, which includes a cylinder body, a guide seal crimped at the right end port of the cylinder body, a piston rod installed inside the cylinder body, a piston assembly mounted at the left end of the piston rod, and a floating piston installed within the cylinder body. The utility model achieves vibration or shock absorption through a buffer chamber, improves processability via a concave surface, and employs a lapped piston, pressure plate, and valve plate. It has good processability and is easy to manufacture.

Description

Title: Compressed Gas Spring with Floating Vibration Damping

Technical Field: The utility model relates to a compressed gas spring with floating vibration damping.

Background Technology: Currently, compressed gas springs have a single structure and lack cushioning and damping effects, resulting in a short service life that affects the lifespan and precision of related equipment. Additionally, the piston structure is complex and costly to process.

Content of the Utility Model: The technical problem to be solved by this utility model is to provide a compressed gas spring with floating vibration damping that is reasonably designed, compact in structure, and easy to use. To solve the above problems, the technical solution adopted by this utility model includes: A compressed gas spring with floating vibration damping, including a cylinder body, a guide seal crimped at the right end port of the cylinder body, a piston rod installed inside the cylinder body, a piston assembly mounted at the left end of the piston rod, and a floating piston installed within the cylinder body; In the cylinder body: the floating piston is located on the left side of the piston assembly, forming a rod chamber between the piston assembly and the guide seal, a non-rod chamber between the piston assembly and the floating piston, and a buffer chamber between the floating piston and the left end of the cylinder body.

Further Improvements to the Technical Solution:

  • A second seal ring that makes sealing contact with the inner wall of the cylinder body is set on the outer side wall of the floating piston.
  • A concave surface is set on the side end face of the floating piston.
  • The piston assembly includes a lapped piston mounted on the piston rod, two pressure plates, and two valve plates;
  • The two valve plates are installed between the two pressure plates, and the lapped piston is installed between the two valve plates.
  • A first seal ring that makes sealing contact with the inner wall of the cylinder body is set on the outer side wall of the lapped piston.
  • At least one vent hole, connecting the rod chamber and the non-rod chamber, is set on the lapped piston.
  • End face notches are set on both side end faces of the lapped piston, with the bottom of the notches connecting to the corresponding vent hole.
  • A right connector is connected to the right end of the piston rod; the cylinder body is filled with inert gas or nitrogen.
  • A left connector is connected to the left end of the cylinder body.

Beneficial Effects: This utility model can meet the requirements of gas springs with damping functions on both sides, especially achieving damping suspension at the end of compression. Therefore, a floating piston is used to isolate part of the original gas chamber into an independent gas chamber filled with inert gas. The amount of gas is calculated according to the user’s required suspension effect, achieving the desired suspension damping effect by adding an airbag at the compression end of the gas spring. First, inject a fixed amount of inert gas for suspension damping from the left connector end of the gas spring, then perform conventional compression inflation from the gap between the piston rod and the guide seal and the cylinder body, and test the calculated force value of the gas spring as usual. This utility model achieves vibration or shock absorption through the buffer chamber, improves processability via the concave surface, and employs a lapped piston, pressure plate, and valve plate. It has good processability and is easy to manufacture.

Description of Drawings:

  • Figure 1 is a structural schematic diagram of the utility model.
  • Figure 2 is a structural schematic diagram of the lapped piston of the utility model.

Where:

  1. Piston Rod
  2. Cylinder Body
  3. Guide Seal
  4. Rod Chamber
  5. Piston Assembly
  6. Pressure Plate
  7. Valve Plate
  8. First Seal Ring
  9. Lapped Piston
  10. Non-Rod Chamber
  11. Buffer Chamber
  12. Left Connector
  13. Floating Piston
  14. Concave Surface
  15. Second Seal Ring
  16. End Face Notch
  17. Vent Hole

Specific Implementation Method: As shown in Figures 1-2, this embodiment of the compressed gas spring with floating vibration damping includes a cylinder body (2), a guide seal (3) crimped at the right end port of the cylinder body (2), a piston rod (1) installed inside the cylinder body (2), a piston assembly (5) mounted at the left end of the piston rod (1), and a floating piston (13) installed within the cylinder body (2); In the cylinder body (2): the floating piston (13) is located on the left side of the piston assembly (5), forming a rod chamber (4) between the piston assembly (5) and the guide seal (3), a non-rod chamber (10) between the piston assembly (5) and the floating piston (13), and a buffer chamber (11) between the floating piston (13) and the left end of the cylinder body (2).

  • A second seal ring (15) that makes sealing contact with the inner wall of the cylinder body (2) is set on the outer side wall of the floating piston (13).
  • A concave surface (14) is set on the side end face of the floating piston (13).
  • The piston assembly (5) includes a lapped piston (9) mounted on the piston rod (1), two pressure plates (6), and two valve plates (7);
  • The two valve plates (7) are installed between the two pressure plates (6), and the lapped piston (9) is installed between the two valve plates (7).
  • A first seal ring (8) that makes sealing contact with the inner wall of the cylinder body (2) is set on the outer side wall of the lapped piston (9).
  • At least one vent hole (17), connecting the rod chamber (4) and the non-rod chamber (10), is set on the lapped piston (9).
  • End face notches (16) are set on both side end faces of the lapped piston (9), with the bottom of the notches (16) connecting to the corresponding vent hole (17).
  • A right connector is connected to the right end of the piston rod (1); the cylinder body (2) is filled with inert gas or nitrogen.

This utility model can meet the requirements of gas springs with damping functions on both sides, especially achieving a damping suspension effect at the end of compression. Therefore, a floating piston (13) is used to isolate part of the original gas chamber into an independent gas chamber filled with inert gas. The amount of gas is calculated according to the user’s required suspension effect, achieving the desired suspension damping effect by adding an airbag at the compression end of the gas spring. First, a fixed amount of inert gas for suspension damping is injected from the left connector (12) end of the gas spring, then conventional compression inflation is performed from the gap between the piston rod (1) and the guide seal (3) and the cylinder body (2), and the calculated force value of the gas spring is tested as usual. This utility model achieves vibration or shock absorption through the buffer chamber (11), improves processability via the concave surface (14), and employs a lapped piston (9), pressure plate (6), and valve plate (7). It has good processability and is easy to manufacture.

Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of this utility model, not to limit them; although the utility model has been described in detail with reference to the above embodiments, those skilled in the art should understand that they can still make modifications to the technical solutions described in the above embodiments, or make some technical features equivalent replacements; it is obvious for those skilled in the art to combine multiple technical solutions of this utility model. These modifications or replacements do not make the essence of the corresponding technical solutions depart from the spirit and scope of the utility model embodiments.

Claims (9) – Compressed Gas Spring with Floating Vibration Damping, invented by LeiYan Gas Spring, a pioneer Chinese Gas Spring Manufacture

A compressed gas spring with floating vibration damping, characterized by: Including a cylinder body (2), a guide seal (3) crimped at the right end port of the cylinder body (2), a piston rod (1) installed inside the cylinder body (2), a piston assembly (5) mounted at the left end of the piston rod (1), and a floating piston (13) installed within the cylinder body (2); Within the cylinder body (2): the floating piston (13) is located on the left side of the piston assembly (5), forming a rod chamber (4) between the piston assembly (5) and the guide seal (3), a non-rod chamber (10) between the piston assembly (5) and the floating piston (13), and a buffer chamber (11) between the floating piston (13) and the left end of the cylinder body (2).

The compressed gas spring with floating vibration damping according to claim 1, characterized by: A second seal ring (15) that makes sealing contact with the inner wall of the cylinder body (2) is set on the outer side wall of the floating piston (13).

The compressed gas spring with floating vibration damping according to claim 1, characterized by: A concave surface (14) is set on the side end face of the floating piston (13).

The compressed gas spring with floating vibration damping according to any one of claims 1-3, characterized by: The piston assembly (5) includes a lapped piston (9) mounted on the piston rod (1), two pressure plates (6), and two valve plates (7); The two valve plates (7) are installed between the two pressure plates (6), and the lapped piston (9) is installed between the two valve plates (7).

The compressed gas spring with floating vibration damping according to claim 4, characterized by: A first seal ring (8) that makes sealing contact with the inner wall of the cylinder body (2) is set on the outer side wall of the lapped piston (9).

The compressed gas spring with floating vibration damping according to claim 5, characterized by: At least one vent hole (17) connecting the rod chamber (4) and the non-rod chamber (10) is set on the lapped piston (9).

The compressed gas spring with floating vibration damping according to claim 6, characterized by: End face notches (16) are set on both side end faces of the lapped piston (9), with the bottom of the notches (16) connecting to the corresponding vent hole (17).

The compressed gas spring with floating vibration damping according to claim 7, characterized by: A right connector is connected to the right end of the piston rod (1); the cylinder body (2) is filled with inert gas or nitrogen.

The compressed gas spring with floating vibration damping according to claim 8, characterized by:

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